CN205401412U - Crankshaft and compressor with same - Google Patents
Crankshaft and compressor with same Download PDFInfo
- Publication number
- CN205401412U CN205401412U CN201620156156.3U CN201620156156U CN205401412U CN 205401412 U CN205401412 U CN 205401412U CN 201620156156 U CN201620156156 U CN 201620156156U CN 205401412 U CN205401412 U CN 205401412U
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- Prior art keywords
- eccentric
- guide groove
- spiral guide
- crankshaft
- eccentric body
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- 238000013459 approach Methods 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 239000010687 lubricating oil Substances 0.000 description 14
- 230000005484 gravity Effects 0.000 description 7
- 239000003921 oil Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000008093 supporting effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000004308 accommodation Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The utility model provides a bent axle and have its compressor, the bent axle, include: the eccentric body is provided with an eccentric bulge, and the eccentric bulge is provided with a spiral guide groove so as to reduce the inertia force of the eccentric body. Because set up the spiral guide slot on eccentric arch, alleviateed the quality of the eccentric body of bent axle, the effectual inertia that has reduced the eccentric body and the friction when other parts of compressor inside take place the friction to the effectual life who prolongs the bent axle.
Description
Technical Field
The utility model relates to a compressor technical field particularly, relates to a bent axle and have its compressor.
Background
The crankshaft in the prior art has limited capability of reducing gravity, and is not beneficial to the frozen lubricating oil at the upper end of the eccentric circle to be smoothly brought to the lower end of the eccentric circle under the action of centrifugal force and external force of the inclined spiral guide groove. In addition, the crankshaft in the prior art has little effect on reducing the mass of the main balance block and the auxiliary balance block, and the cost of used materials is high.
Furthermore, the crankshaft in the prior art is provided with an oil hole, and the spiral oil groove in the prior art needs to supply oil through the oil hole at the eccentric circle of the crankshaft. The lower end of the eccentric circle of the crankshaft and the lower flange cannot support the compressor pump body assembly, so that the abrasion of the thrust surface of the crankshaft of the compressor is aggravated.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a bent axle and have its compressor to solve the easy problem of wearing and tearing of the thrust surface of bent axle among the prior art.
In order to achieve the above object, according to an aspect of the present invention, there is provided a crankshaft comprising: the eccentric body is provided with an eccentric bulge, and the eccentric bulge is provided with a spiral guide groove so as to reduce the inertia force of the eccentric body.
Furthermore, the spiral guide groove is arranged on the eccentric bulge in a penetrating way along the axial direction of the eccentric bulge.
Further, the spiral guide groove spirally rises along the axial direction of the eccentric protrusion, the spiral angle of the spiral guide groove is alpha, and,wherein H is the height of the eccentric body; and L is the length of a connecting line between the central line at the opening at one end of the spiral guide groove and the central line at the opening at the other end of the spiral guide groove.
Further, the spiral guide groove spirally ascends from one end of the eccentric protrusion toward the other end of the eccentric protrusion in the axial direction of the eccentric protrusion and gradually approaches the geometric center of the eccentric body.
Further, the geometric center is the center of a circle of the eccentric body.
Further, the area of the cross section of the spiral guide groove gradually increases along one end of the eccentric protrusion toward the other end of the eccentric protrusion.
Further, the crankshaft further includes: a long shaft part connected with one end of the eccentric protrusion; and the short shaft part is connected with the other end of the eccentric bulge and is coaxially arranged with the long shaft part.
Further, an extension line of a center line of a cross section in a radial direction of the eccentric body of the spiral guide groove is located on one side of a center of the eccentric body.
Furthermore, an included angle beta is formed between a connecting line of the outer edge of the spiral guide groove farthest from the circle center and the side edge of the spiral guide groove where the outer edge farthest from the circle center is located, and the spiral guide groove is located on one side of the connecting line.
Further, 0 < β < 90 °.
Further, the spiral guide groove is a plurality of, and a plurality of spiral guide grooves set up on the eccentric arch.
Further, the cross section of the spiral guide groove is wedge-shaped or triangular.
According to another aspect of the present invention, there is provided a compressor, including a crankshaft, the crankshaft being the above crankshaft.
Further, the compressor further includes: a cylinder having an accommodating chamber; the roller is arranged in the accommodating cavity and provided with an inner cavity; wherein, eccentric body is located the inner chamber, forms the high pressure zone in order to prevent eccentric body wearing and tearing between the lateral wall of outer peripheral surface and inner chamber and the chamber bottom of holding of eccentric body.
Use the technical scheme of the utility model, a bent axle and have its compressor is provided, the spiral guide slot has been seted up on the eccentric arch on the eccentric body of bent axle. Because set up the spiral guide slot on eccentric arch, alleviateed the quality of the eccentric body of bent axle, the effectual inertia that has reduced the eccentric body and the friction when other parts of compressor inside take place the friction to the effectual life who prolongs the bent axle.
Drawings
The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 shows a schematic structural view of an embodiment of a crankshaft according to the present invention;
FIG. 2 shows an enlarged schematic view at B in FIG. 1;
FIG. 3 is a schematic cross-sectional view taken along line A-A of FIG. 1;
fig. 4 shows a schematic structural view of another perspective of an embodiment of a crankshaft according to the present invention; and
fig. 5 shows a schematic structure diagram of a shaft system of a compressor part according to the present invention.
Wherein the figures include the following reference numerals:
10. an eccentric body; 11. an eccentric protrusion; 12. a spiral guide groove; 20. a long shaft portion; 30. a short shaft portion.
Detailed Description
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
As shown in fig. 1 and 4, according to an embodiment of the present invention, a crankshaft is provided. The crankshaft includes an eccentric body 10, and the eccentric body 10 has an eccentric protrusion 11. The eccentric protrusion 11 is provided with a spiral guide groove 12 to reduce the inertia force of the eccentric body 10.
In this embodiment, since the spiral guide groove 12 is disposed on the eccentric protrusion 11, the mass of the eccentric body 10 of the crankshaft is reduced, and the inertia force of the eccentric body 10 and the friction force generated when the eccentric body 10 rubs against other parts inside the compressor are effectively reduced, thereby effectively prolonging the service life of the crankshaft.
The spiral guide groove 12 is opened in the eccentric protrusion 11 so as to penetrate in the axial direction of the eccentric protrusion 11. The arrangement can realize that the refrigeration lubricating oil is conveyed from one end of the eccentric body 10 to the other end of the eccentric body 10 and is used for lubricating a contact surface of the eccentric body 10, which is contacted with other parts when in friction, thereby effectively reducing the friction force and the damage degree of the eccentric body 10.
Preferably, the spiral guide groove 12 is spirally raised in the axial direction of the eccentric protrusion 11, the spiral angle of the spiral guide groove 12 is α, and,where H is the height of the eccentric body 10. L is a helical guideThe length of the connecting line between the center line at the opening at one end of the groove 12 and the center line at the opening at the other end of the spiral guide groove 12. As shown in fig. 1 and 2, FG and KJ in fig. 2 are widths of both end openings of the spiral guide groove 12, respectively, and a straight line L shown in the drawing is a line length of a center line of the widths of both end openings. The arrangement is such that, when the eccentric body 10 is rotated at a high speed, the frozen lubricating oil located at the upper end of the eccentric body 10 is carried from the upper end of the spiral guide groove 12 to the lower end of the eccentric body 10 by the centrifugal force generated by the rotation of the eccentric body 10.
Further, the spiral guide groove 12 spirally ascends from one end of the eccentric protrusion 11 toward the other end of the eccentric protrusion 11 in the axial direction of the eccentric protrusion 11 and gradually approaches the geometric center of the eccentric body 10. This arrangement further effectively achieves that the frozen lubricating oil can be smoothly brought from the upper end of the eccentric body 10 to the lower end of the eccentric body 10. Preferably, the geometric center is the center of the eccentric body 10.
In the present embodiment, the area of the cross section of the spiral guide groove 12 gradually increases along one end of the eccentric protrusion 11 toward the other end of the eccentric protrusion 11. This arrangement is advantageous for increasing the pressure of the frozen lubricating oil.
As shown in fig. 1, the crankshaft further includes a long shaft portion 20 and a short shaft portion 30. The long shaft portion 20 is connected to one end of the eccentric protrusion 11. The short shaft portion 30 is connected to the other end of the eccentric protrusion 11 and is disposed coaxially with the long shaft portion 20. The cross-sectional area of the spiral guide groove 12 gradually increases from one end where the long shaft portion 20 is provided toward the other end where the short shaft portion 30 is provided. This arrangement further facilitates the flow of the frozen lubricating oil and thus enables an effective lubrication.
As shown in fig. 3, the extension line of the center line of the spiral groove 12 in the cross section in the radial direction of the eccentric body 10 is located on one side of the center of the eccentric body 10. The arrangement is favorable for the eccentric body 10 to rotate under the driving of the crankshaft, and the central line of the spiral guide groove 12 is positioned on one side of the circle center of the eccentric body 10, so that the refrigeration lubricating oil in the spiral guide groove 12 deviating from the circle center of the eccentric body 10 can be well and smoothly taken from the other end of the eccentric body 10.
Preferably, a line between the outer edge of the spiral guide groove 12 farthest from the center of the circle and the center of the circle has an included angle β with the side of the spiral guide groove 12 where the outer edge farthest from the center of the circle is located, and the spiral guide groove 12 is located at one side of the line. Preferably, 0 < β < 90 °. The arrangement enables the frozen lubricating oil in the spiral guide groove 12 to flow under the centrifugal force generated by the eccentric body 10, and effectively utilizes the gravity of the frozen lubricating oil, so that the frozen lubricating oil flows more smoothly from the end provided with the long shaft part 20 to the end provided with the short shaft part 30 under the resultant force of the centrifugal force and the gravity of the frozen lubricating oil. In order to enable the crankshaft to provide sufficient frozen lubrication oil, the spiral guide groove 12 may be provided in plurality, and a plurality of spiral guide grooves 12 are provided on the eccentric protrusion 11.
Further, in order to reduce the resistance of the spiral guide groove 12 in the process of rotating with the crankshaft at a high speed and to enable the lubricating and freezing oil to smoothly flow from the upper end of the eccentric body 10 to the lower end of the eccentric body 10, when the compressor crankshaft rotates clockwise at a certain rotating speed omega, an angle beta formed by a plane on which a BD point connecting line is located and a connecting line from a B point on an eccentric circle of the crankshaft to a central point O' on which a long shaft and a short shaft are located should satisfy 0 & lt beta & lt 90 deg.
As shown in fig. 3, the spiral guide groove 12 has a wedge-shaped cross section. Of course, the cross section of the spiral guide groove 12 may also be a triangular structure, that is, when the line D, E, C is a straight line in the figure, the cross section of the spiral guide groove 12 may also be a triangular structure. Of course, the connecting lines among the points B, C, D and E may be straight lines or curves.
The points G and F of the spiral guide groove 12 may be disposed near the center line where the long axis and the short axis of the crankshaft are located, and the points K and J of the spiral guide groove 12 are disposed far from the center line where the long axis and the short axis of the crankshaft are located. Like this, the frozen lubricating oil of the upper end of the eccentric body 10 of bent axle is taken to the lower extreme of eccentric body 10 under the effect of spiral guide slot 12 and centrifugal force, thereby frozen lubricating oil forms the high pressure region at the cylinder side at bent axle thrust surface place, the bottom of lower flange plane promptly compressor cylinder, the roller inner chamber and the lower extreme of the eccentric body 10 of bent axle, because the high pressure region has ascending thrust, when the pressure in the high pressure region is enough big, can jack-up the lower extreme of eccentric body 10 so that eccentric body 10 plays the effect of supporting compressor pump body subassembly, because the lower extreme of eccentric body 10 at this moment does not take place the contact with the cylinder bottom, promptly do not take place the friction, so great reduction the frictional force between eccentric body 10 and the inside spare part of compressor, the effectual performance that improves the compressor.
The crankshaft in the above embodiments may also be used in the technical field of compressors, that is, according to another embodiment of the present invention, there is provided a compressor, including a crankshaft, where the crankshaft is the crankshaft in the above embodiments. The compressor further includes a cylinder and a roller. The cylinder has an accommodation chamber. The roller is arranged in the accommodating cavity and is provided with an inner cavity. Wherein, the eccentric body 10 is located in the inner cavity, and a high pressure area is formed between the outer circumferential surface of the eccentric body 10 and the side wall of the inner cavity and the bottom of the accommodating cavity to prevent the eccentric body 10 from being worn.
In this embodiment, the spiral guide groove 12 rotates with the crankshaft at a high speed, so that the frozen lubricant oil at the upper end of the eccentric circle of the crankshaft is smoothly brought to the lower end of the eccentric body 10, which is the eccentric circle of the crankshaft, under the action of centrifugal force and external force of the spiral guide groove 12, and a high-pressure area is formed in a cavity formed by the cylindrical side surface where the thrust surface of the crankshaft is located, the lower flange plane, which is the bottom surface of the cylinder, the inner cavity of the roller and the lower end of the eccentric circle of the crankshaft. The eccentric body 10 has a certain supporting effect on the compressor pump body assembly in the vertical direction, and shares the gravity of the crankshaft thrust surface. On the other hand, the spiral guide groove 12 rotates at a high speed along with the crankshaft, the frozen lubricating oil provides the rising reaction force for the spiral guide groove 12, the gravity borne by the thrust surface of the crankshaft is further reduced, meanwhile, the friction force between the eccentric circle of the crankshaft and the inner cavity of the roller is reduced, and the reliability of the compressor is further improved.
Furthermore, the mass of the eccentric body 10 and the main and auxiliary balance blocks is reduced, the gravity borne by the crankshaft thrust surface is reduced, the friction force of the eccentric body 10 is further reduced, and the power consumption and the inertia force of the compressor are effectively reduced.
As shown in fig. 5, the equilibrium equations of force and moment of this force system can be established according to the mechanics principle:
FIr1+FIr＝FIr2γ……(1)
FIr1L1＝FIrL2………(2)
in the above formula: m is1、m2、mrMass of the auxiliary balance weight, the main balance weight and the eccentric circle, respectively, FIr1For the rotating inertial force of the auxiliary balance weight, FIrFor deflection of crankshaftCentral circle rotational inertia force, FIr2Is a rotational inertia force of the auxiliary balance weight, L1Is the distance between the primary and secondary balance blocks, L2Is the distance from the eccentric body 10 to the main balance weight, r is the distance from the eccentric center of mass of the crankshaft to the center of the crankshaft, gamma is the distance from the center of mass of the eccentric body 10 of the crankshaft to the center of the crankshaft, r1 is the distance from the center of mass of the auxiliary balance weight to the center of the crankshaft, and r2 is the distance from the center of mass of the main balance weight to the center of the crankshaft.
From the above formula, it can be seen that: the mass of main, vice balancing piece all receives eccentric body 10 promptly eccentric circle mass's influence, if reduce eccentric circle mass, the mass of main, vice balancing piece all reduces to reduce the gravity that the bent axle thrust surface bore, and then reduce the frictional force between bent axle thrust surface and lower flange plane, reduced the compressor consumption and improved the reliability of bent axle thrust surface.
Since the eccentric portion of the crankshaft and the center of mass of the roller do not coincide with the main rotation center, the compressor generates rotational inertia force during operation. Namely, it is
FIr2＝FIr1+FIr＝m1r1ω2+mrrω2……(5)
Therefore, the mass of the eccentric body 10 is reduced, that is, the inertial force of the compressor is reduced, which is beneficial to the stable operation of the compressor.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (14)
1. A crankshaft, comprising:
the eccentric body (10) is provided with an eccentric protrusion (11), and the eccentric protrusion (11) is provided with a spiral guide groove (12) to reduce the inertia force of the eccentric body (10).
2. A crankshaft according to claim 1, characterized in that the helical guide groove (12) opens through the eccentric protrusion (11) in the axial direction of the eccentric protrusion (11).
3. A crankshaft according to claim 1, characterized in that the helical groove (12) spirals in the direction of the axis of the eccentric lobe (11), the helix angle of the helical groove (12) being a, and,
wherein,
h is the height of the eccentric body (10);
l is the length of a connecting line between a center line at an opening at one end of the spiral guide groove (12) and a center line at an opening at the other end of the spiral guide groove (12).
4. A crankshaft according to claim 1, characterized in that the spiral guide groove (12) spirals in the axial direction of the eccentric protrusion (11) from one end of the eccentric protrusion (11) towards the other end of the eccentric protrusion (11) and gradually approaches the geometric center of the eccentric body (10).
5. A crankshaft according to claim 4, characterized in that the geometric centre is the centre of the eccentric body (10).
6. A crankshaft according to claim 1, characterized in that the area of the cross section of the spiral guide groove (12) is gradually increased along one end of the eccentric protrusion (11) toward the other end of the eccentric protrusion (11).
7. The crankshaft of claim 1, further comprising:
a long shaft part (20) connected with one end of the eccentric protrusion (11);
and a short shaft part (30) connected to the other end of the eccentric protrusion (11) and disposed coaxially with the long shaft part (20).
8. A crankshaft according to claim 7, characterized in that the extension of the centre line of the helical guide groove (12) in a cross section in the radial direction of the eccentric body (10) is located on one side of the centre of the eccentric body (10).
9. A crankshaft according to claim 8, characterized in that the connecting line of the outer edge of the spiral guide groove (12) farthest from the center of the circle and the center of the circle has an angle β with the side of the spiral guide groove (12) where the outer edge farthest from the center is located, the spiral guide groove (12) being located at one side of the connecting line.
10. A crankshaft according to claim 9, wherein 0 < β < 90 °.
11. A crankshaft according to claim 1, wherein said spiral guide groove (12) is plural, and a plurality of said spiral guide grooves (12) are provided on said eccentric protrusion (11).
12. A crankshaft according to claim 1, characterized in that the cross-section of the helical guide groove (12) is wedge-shaped or triangular.
13. A compressor comprising a crankshaft, characterized in that it is a crankshaft according to any one of claims 1 to 12.
14. The compressor of claim 13, further comprising:
a cylinder having an accommodating chamber;
a roller disposed within the receiving cavity, the roller having an inner cavity;
wherein the eccentric body (10) is positioned in the inner cavity, and a high-pressure area is formed between the outer peripheral surface of the eccentric body (10) and the side wall of the inner cavity and the bottom of the accommodating cavity to prevent the eccentric body (10) from being worn.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620156156.3U CN205401412U (en) | 2016-02-29 | 2016-02-29 | Crankshaft and compressor with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620156156.3U CN205401412U (en) | 2016-02-29 | 2016-02-29 | Crankshaft and compressor with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205401412U true CN205401412U (en) | 2016-07-27 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620156156.3U Active CN205401412U (en) | 2016-02-29 | 2016-02-29 | Crankshaft and compressor with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205401412U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105570277A (en) * | 2016-02-29 | 2016-05-11 | 珠海凌达压缩机有限公司 | Crankshaft and compressor with same |
-
2016
- 2016-02-29 CN CN201620156156.3U patent/CN205401412U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105570277A (en) * | 2016-02-29 | 2016-05-11 | 珠海凌达压缩机有限公司 | Crankshaft and compressor with same |
| CN105570277B (en) * | 2016-02-29 | 2019-02-22 | 珠海凌达压缩机有限公司 | Crankshaft and compressor with same |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |